Machine drive



June 17, 1952 M. SHAPIRO 2,600,929

\ MACHINE DRIVE Filed March 24, 1949 I 2 SHEETSSHEET 1 IN V EN TOR.

MORDECAI SNAP] R0 BY M ck M A TTOENE Y5 M. SHAPIRO MACHINE DRIVE June17, 1952 2 SHEETS-SHEET 2 Filed March 24, 1949 WM w vw I A Q M MWPatented June 17, 1952 UNITED STATES PATENT OFFICE MACHINE DRIVEMordecai Shapiro, Merrick, N. Y.

Application March 24, 1949, Serial No. 83,221

3 Claims. 1

My invention relates to a new and improved drive for machines, such assewing machines and other machines.

It is well-known to provide alined driving and driven shafts which haverespective coupling members or clutch members fixed respectivelythereto, and to move the driven shaft axially relative to the drivingshaft, in order to connect said driven shaft operatively to said drivingshaft or to disconnect said driven shaft from said driving shaft.

According to one embodiment of my invention, I provide the periphery ofthe driven shaft with two continuous and circumferential grooves whichare spaced axially from each other, so that said periphery operates asthe inner race of a ball-bearing. I provide the internal periphery ofthe outer race with two continuous and circumferential grooves, each ofwhich is opposite a respective groove of the inner race. A part of eachball is located in a groove of the inner race, and a part of each ballis located in the corresponding groove of the outer race.

This outer race, which does not rotate with the driven shaft, preferablyhas an external cylindrical periphery, and it fits closely and axiallyslidably in an external guide. I apply the axial force directly to saidouter race, in order to shift the driven shaft axially between itsconnected and disconnected positions. I thus provide a device in whichthe anti-friction bearing provides an axial thrust member for shiftingthe driven shaft axially from one position to the other.

I prefer to locate the outer race in an outer sleeve-housing, which hasend-portions which extend axially beyond the race, and to provide saidend-portions of said sleeve-housing with respective oil-seals, so thatthe bearing can always be filled with lubricating oil.

Other objects and advantages of my invention are disclosed in theannexed description and drawings, which illustrate a preferredembodiment thereof.

Fig. 1 is a side elevation, which shows the improved drive inassociation with a sewing machine;

Fig. 2 is an end view, taken at the right of Fig. 1;

Fig. 3 is a section on the line 3-3 of Fig. 2, showing the driven shaftuncoupled from the driving shaft, and showing the brake in operativeposition;

Fig. 4 is similar to- Fig. 3, showing the driven shaft coupled to thedriving shaft, and showing the brake in non-operative position;

Figs. 5 and Gare respective sections on the lines 5-5 and 6-6 of Fig. 3;and

Fig. '7 is a detail sectional View of the improved anti-frictionbearing.

Fig. 1 shows a table I, to which for example, a sewing machine 2 isfixed. This sewing machine 2 is provided with the usual drive pulley 3,which is connected by a belt l to a pulley 5 which is fixed to a drivenshaft ii of the drive mechanism or drive unit. This drive unit isenclosed in a casing I. fastening members 8 to the casing 9 of a drivingmotor.

Fig. 3 shows a part of the driving shaft I0 of said motor. A drivingrotor H is fixed detachably to theshaft ID by one or more set screws 2.A friction member [4, of frusto-conical shape, is fixed detachably tothe rotor II by means of fastening members it. A hollow driven rotor I6is detachably fixed to the driven shaft 6, by one or more set screws [7.The shafts ID and 6 are coaxial. Shaft 6 is axially movable relative toshaft Ill.

These rotors II and i6 exemplify conventional clutch or couplingmembers, to which the invention is not limited, as I can use any type ofclutch means or coupling means.

As shown in Fig. 7, the driven shaft 6 is provided with twocircumferential and continuous grooves i8, which are in planes which areperpendicular to the common axis of shafts l0 and 6. The periphery ofshaft 6 provides the inner race of an antifriction bearing, whichcomprises also an outer sleeve-race 2B, which is fixed eitherpermanently or releasably to sleeve housing I9, so that outersleeve-race 26 and sleeve housing [9 rotate in unison, and also moveaxially in unison. In effect, the sleeve housing I9 is a. part of outersleeve-race 20. Said sleeve l9 extends axially beyond race 2%) toprovide end-extensions of the race.

In this embodiment, the inner periphery of outer sleeve-race 20 is acylinder. This is provided with two internal circumferential andcontinuous grooves 20a, which are in planes which are perpendicular tothe axis of sleeve-race 20.

Each groove I8 is associated with a respective set or series ofanti-friction balls B. Each ball B is located partially in a respectivegroove l8. Each ball B interfits rotatably with the wall of itsrespective groove l8. The set or series of anti-friction balls Bassociated with each groove I8 is also associated with a groove 20a.Each ball B is located partially in a respective groove 20a. Each ball Binterfits rotatably with the wall of its respective groove 2M.

This casing l is afiixed by means of The sleeve-housing I9 and the race26 may be resilient, so that they can be easily assembled by means of africtional drive-fit. The assembly of sleeve-housing I3 and race 20 mayalso be resilient, so that the balls B can be easily forced into thefinal assembled position of Fig. 7. Also, the race 20 may consist of twolongitudinal halfparts, which may be fixed to each other detachably.

A substantial part of each ball B is located in its respective groovesI8 and 20a, so that race 20 and shaft 6 move axially in unison under theoperating conditions. If desired, the end-portions of race 20 may beprovided with one or more axial slits, in order to increase their radialflexibility.

In an ordinary drive for a sewing machine, which requires low drivingforce, many of these features are not required. In such case, and as oneexample, the diameter of balls B is of an inch, the depth of each grooveI8 is 1 of an inch, the clearance between race and shaft 6 is 1 of aninch, and the depth of each groove 20a is I16 of an inch. In such case,the thickness of race 2!] is /4 of an inch, and the thickness ofsleeve-housing I9 is 6% of an inch. The race 20 is made of hardenedsteel and the sleeve I9 is made of hardened steel.

In such case, the race 23 and the sleeve-housing I9 may be initiallyassembled by friction as a sub-unit, which is then easily assembled withballs B, because this sub-unit has suiflcient radial flexibility withoutproviding any axial slit or slits in the end-portions of race 20.

The sleeve I9, which may optionally be omitted,

is used because it has end-portions which extend axially beyond the race20, thus providing means for assembly with the outer angular members 2Iaand the inner angular members 2ib of respective channels 2I. Theseangular members 2 Ia and 2 I?) are spaced slightly from shaft 6.

Each outer angular member 2Ia has a cylindrical flange which has a tightfriction fit in sleeve-housing I9, and a planar radial flange The edgeof each said cylindrical flange abuts the respective end-wall of race20.

Each said inner angular member 2Ib has a cylindrical flange which has atight friction fit in the cylindrical flange of the respective outerangular member ZI a. The edge of the cylindrical flange of each innerangular member 2 ID optionally abuts the planar radial flange of therespective outer angular member 2 Ia. Each said inner angular member 2Ibhas a radial planar flange which abuts the respective end-wall of race29.

A resilient and flexible and compressible sealing gasket 22, which ismade of impregnated felt or other suitable material, is held in eachchannel 2I, in order to provide an oil seal. In the final assembly, eachgasket 22 abuts the shaft 6 under slight compression.

The angular members 2Ia and 2Ib and their respective sealing gaskets 22may be assembled as respective sub-units, which can be pushed intoassembled position. I can thus provide a filling of lubricating oil inthe anti-friction bearing. Each channel 2I and its gasket 22 can beremoved, in order to replenish this oil filling.

The cylindrical sleeve housing I9 fits closely and slidably in acylindrical recess of casing I. Said recess has a cylindrical wall 1c,which has a bottom axial slot or opening la.

A lever 24 is pivoted by a pivot pin 25 to the walls of a slot in casingI. Said lever 24 has an arm 23 which extends through said slot of casingI and through the slot or opening Ia. When the driven shaft 6 isuncoupled from driving shaft ID, as illustrated in Fig. 3, said arm 23abuts sleeve housing I9, and said arm 23 is vertical. This arm 23 may beresilient and compressible. When arm 23 is in its position of Fig. 3,the tip of arm 23 may be slightly spaced from sleevehousing I9.

When lever 24 is turned from the position of Fig. 3 to the position ofFig. 4, the arm 23 frictionally forces sleeve housing I9 axially towardsdriven shaft I0, thus forcing driven shaft 6 and its coupling member I6to the coupling position shown in Fig. 4 by means of outer-sleeve race2! and balls B, thus rotating driven shaft 6 while the outer sleeve-race2E and sleeve-housing I9 are held against rotation by the friction ofarm 23. The inner face of arm 23 may be provided with a resilient andcompressible friction strip, in order to provide the frictional thrust.

The sleeve housing I9 and lever 24 are normally maintained in theirrespective positions of Fig. 3 by a compression spring 33. One end ofcompression spring 33 abuts sleeve-housing I9. The other end ofcompression spring 33 abuts a plate 34 which is fixed to the innerend-face of wall 'Ic by screws 35.

One end of lever 24 is connected by a double, adjustable rod assembly30, or other connecting member, to a grilled treadle 3I, which ispivoted by a pivot pin 32 to a fixed base.

A plate 2'! has a slot 29a. Said plate 21 is fixed adjustably to lever24 by a clamping screw 26, Whose shank extends through slot 29a.

Plate 21 has a brake-shoe 28, which is provided with a brake-strip 29.Said plate 21 is movable through a slot or opening lb of casing I.

When lever 24 is turned to the position of Fig. 4, the brake is releasedfrom the driven coupling member I6. When lever 24 is in its normalposition of Fig. 3, the brake is applied to coupling member I6.

Fig. 2 also shows means for tightening the drive belt 4 between thedriven pulley 3 and the drive pulley 5.

A bracket 35 is fixed to the inner side of the table I. This bracket 36has a depending arm 31. A part-cylindrical flange 38 is detachably fixedto the exterior of the motor casing 9 by fastening members 39. Thisflange 38 has a pair of lugs 43, between which the depending arm 31 islocated. The lugs 40 are adjustably connected to the arm 31, by means ofthe pivot bolt or pivot clamping screw 4| which can be tightened, inorder to clamp the lugs 40 and arm 31 to each other in adjustedposition. Said flange 38 has a pair of spaced arms 42. A clamping screw43 is connected to each arm 42. Each clamping screw 43 has a shank whichextends through the curved slot 44 of a respective arm 45 which isintegral with the bracket 35. The motor housing 9 can therefore besecurely clamped in adjusted position, at which the belt 4 is underproper tension.

The invention is not restricted to any type of anti-friction member, orto a solid shaft which extends through an external hollow race. Theinvention also includes the sub-combinations disclosed herein.

I have disclosed a preferred illustrative embodiment of my invention,but numerous changes and omissions and additions can be made withoutdeparting from its scope.

I claim:

1. In combination, a rotatable shaft which has an outer periphery whichha two circumferential and continuous shaft grooves, said shaft groovesbeing located in planes which are perpendicular to the axis of rotationof said shaft, a hollow external race through which said shaft extendsaxially, said race having a cylindrical inner periphery, said racehaving two internal circumferential and continuous race-grooves, saidracegrooves being located in planes which are perpendicular to the axisof rotation of said race, each of said race-grooves opposing and beingpaired with a respective shaft groove, a set of rotatable anti-frictionmembers associated with each said pair of grooves, a part of each ofsaid anti-friction members being located in its respective shaft groove,a part of each of said antifriction members being located in itsrespective race-groove, said anti-friction members interfittingrotatably with the walls of said shaft grooves and with the walls ofsaid race-grooves, said shaft being movable to and fro in the directionof said axis in unison with said hollow external race and said sets ofanti-friction members.

2. A rotatable shaft which has an outer periphery which has twocircumferential and continuous shaft grooves, said shaft grooves beinglocated in planes which are perpendicular to the axis of rotation ofsaid shaft, a hollow external race through which said shaft extendsaxially, said race having a cylindrical inner periphery, said racehaving two internal circumferential and continuous race-grooves, saidrace-grooves being located in planes which are perpendicular to the axisof rotation of said race, each of said race-grooves opposing and beingpaired with a respective shaft groove, a set of rotatable antifrictionmembers associated with each said pair of grooves, a part of each ofsaid anti-friction members being located in its respective shaft groove,a part of each of said anti-friction members being located in itsrespective race-groove, said anti-friction members interfittingrotatably with the walls of said shaft grooves and with the walls ofsaid race-grooves, said race having endextensions, and an oil seallocated in each of said end-extensions, each oil seal comprising a pairof angle members which constitute a channel, the angle member of eachpair interfitting with each other and abutting a respective shoulder,each said channel having a sealing gasket located therein, each saidsealing gasket extending radially beyond the respective channel andabutting the outer periphery of said shaft.

3. A combination according to claim 1, said race being sufiicientlyresilient to snap said antifriction members into their aforesaidpositions when said race-grooves are respectively alined with said shaftgrooves.

MORDECAI SHAPIRO.

REFERENCES CITED The following references are of record in the file ofthis patent:

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